JPH0545816B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an electric chain block having a two-stage planetary gear transmission used for transporting various types of cargo.

[Conventional technology]

Conventionally, as an example of a planetary gear type two-stage transmission,
As disclosed in Japanese Unexamined Patent Publication No. 59-231246, a cylindrical body of a carrier hub is fitted to a hollow input shaft via a bearing, and a drive hub having a support cylinder disposed outside the cylindrical body is provided. , a plurality of planetary gears are fitted and fixed to the hollow input shaft, a plurality of planetary gears are attached to the carrier hub, an annular sun gear that meshes with the planetary gears is fitted and fixed to the outside of the support cylinder, and a ring gear is meshed with each planetary gear. Structures with similar structures are known.

However, in the case of the conventional two-stage planetary gear transmission, the cylindrical body of the carrier hub is fitted onto the outside of the hollow input shaft via a bearing, and the support cylindrical body of the drive hub is disposed outside the cylindrical body. Since the sun gear is fitted and fixed on the outside of the support cylinder, the diameter of the sun gear becomes considerably large, which causes a problem in that a large reduction ratio cannot be obtained.

[Purpose and structure of the invention]

This invention can increase the reduction ratio,
It is an object of the present invention to provide an electric chain block having a two-stage planetary gear transmission with good weight balance. a hollow shaft 34 having a load sheave 32 around which a load chain is wound, a driven shaft 5 is rotatably inserted therethrough, and the annular support member rotatably supports a planetary gear 3 meshing with the sun gear 2; 4
A control member 7, which is non-rotatably connected to one end of a driven shaft 5 protruding from one end of the hollow shaft 34 and includes an internal gear 6 that meshes with the planetary gear 3, is connected to the drive shaft 1. The control member 7 is rotatably and slidably fitted, and the control member 7 is provided with a removable connection coupling portion to the annular support member 4 and a control coupling portion that is detachable to a fixed portion such as the transmission frame 8. The coupling of the control member 7 to the annular support member 4 and the control member 7 from said fixed part are caused by the magnetization and demagnetization of one electromagnetic coil 9.
The control member 7 is coupled to the fixed portion and the control member 7 is separated from the annular support member 4, and the hollow shaft
the other end of the driven shaft 5 protruding from the other end;
The electric chain block has a planetary gear type two-stage transmission characterized in that a gear reduction mechanism is provided between the hollow shaft 34 and the other end thereof.

〔Example〕

Next, the present invention will be explained in detail using illustrated examples.

1 to 3 show a first embodiment of the present invention, and are shown in the front-rear direction (Fig. 1 to 3).
One end (rear end) of the drive shaft 1 extending in the left-right direction in the figure is connected to the rotor shaft 11 of the electric motor 10 with an electromagnetic brake, and a hollow shaft 34 extending in the front-rear direction
A load sheave 33 around which a load chain (not shown) is wound is integrally provided on the outside of the intermediate portion of the hollow shaft 34, and both longitudinally opposite portions of the hollow shaft 34 are connected to the frame 4 of the electric chain block.
5 rotatably supported via a bearing 35,
A driven shaft 5 is inserted through the hollow shaft 34, and a flange 12 is integrally provided at one end of the driven shaft 5 protruding from one end (rear end) of the hollow shaft 34.

A sun gear 2 is formed at the other end (front end) of the drive shaft 1, and the other end (front end) of the drive shaft 1 is
A driven shaft 5 arranged on the same straight line as the driving shaft 1
A plurality of planetary gears 3 are inserted into holes at one end via bearings and meshed with the sun gear 2, and are rotatably attached to an annular support member 4, which is connected to one end of the driven shaft 5. It is fixed by bolts 13 to a flange 12 provided on the flange 12 .

A control member 7 is provided on the outer periphery of the annular support member 4 with a frusto-conical friction surface 14 that expands toward the front, and is composed of a cylindrical body 15 and an annular disc body 16 integrally provided at its front end. A cylindrical body 15 is rotatably fitted to the drive shaft 1 via a bearing 17, and is removably fitted to the frusto-conical friction surface 14 at the front portion of the outer peripheral side of the annular disk body 16. A frusto-conical cylindrical friction ring 18 is fixed,
The frusto-conical friction surface 14 and the frusto-conical cylindrical friction ring 18 constitute a detachable connecting joint.

The internal gear 6 that meshes with the planetary gear 3 is fixed to the annular disk 16 by bolts 19 inside the truncated conical cylindrical friction ring 18, and a transmission is attached to the outer peripheral rear portion of the annular disk 16. Friction surface 21 at the front of the inner flange 20 in the frame 8
An annular friction plate 22 that is removably engaged with is fixed to the annular friction plate 22, and the friction surface 21 and the annular friction plate 22 constitute a removable control coupling portion.

Annular holding member 23 holding electromagnetic coil 9
is in contact with the rear surface of the inner flange 20 and the bolt 2
A bearing 26 is fitted inside the annular attracted body 25 made of magnetic material and is fixed by a snap ring 27 and is arranged to face the rear surface of the annular holding member 23 .
is fitted and locked to a support ring 28 fitted to the rear outer periphery of the cylinder 15, and a thrust ring 29 that engages with the rear end surface of the bearing 26 is fitted to one end of the cylinder 15. Along with that thrust ring 2
A snap spring 30 that locks 9 is fitted and locked.

A tightening spring 31 made of a helical spring for tightening the connecting joint is interposed between the annular disc body 16 and the support ring 28, and a tightening spring 31 is interposed between the annular holding member 23 and the annular attracted body 25. A return spring 32 made of a helical spring for pushing back the annular attracted object 25 in a direction away from the electromagnetic coil 9 (rearward) is interposed between the recess and the recess.

A driven gear 46 on the outside of the other end of the hollow shaft 34
A drive gear 47 is formed on the other end of the driven shaft 5 which is fitted and fixed and projects from the other end of the hollow shaft 34, and an intermediate driven gear 48 that meshes with the drive gear 47 meshes with the driven gear 46. An intermediate drive gear (not shown) is fixed to the intermediate shaft, and the drive gear 47, the intermediate driven gear 48, the intermediate drive gear, and the driven gear 46 constitute a gear reduction mechanism.

A mechanical brake device is provided between the driven shaft 5 and the hollow shaft 34 to prevent the load sheave 33 from rotating in reverse due to the load of the suspended load. Since this is well known, illustration and detailed explanation thereof will be omitted. In addition, a load sheave 3 is mounted on the upper part of the frame 45 in the electric chain block.
3 above the chain block support fitting 49
are connected by a pin 50.

In the electric chain block having the planetary gear type two-stage transmission of the first embodiment, when the electromagnetic coil 9 is demagnetized, as shown in FIG.
2, the annular attracted body 25 made of magnetic material is moved to the retreat position, and the annular attracted body 25
As the control member 7 is moved backward via the snap ring 27, the bearing 26, the thrust ring 29, and the snap ring 30, the frusto-conical cylindrical friction ring 18 of the control member 7 engages the frusto-cone friction surface 14 of the annular support member 4. The frictional connection between the annular support member 4 and the annular disc 16 of the control member 7 is released, and the friction surface 21 of the annular disc 16 is brought into contact with the friction surface 21 of the inner flange 20 of the transmission frame 8. When pressed, the control member 7 and the transmission frame 8 are frictionally connected.

When the electric motor 10 with an electromagnetic brake is operated in this state and the drive shaft 1 is rotated, the drive shaft 1 rotates the planetary gear 3 via the sun gear 2, and the planetary gear 3 turns around the sun gear 2. However, since the annular support member 4 supporting the shaft of the planetary gear 3 is rotated at low speed by the rotation of the planetary gear 3, the rotation of the drive shaft 1 is decelerated by the planetary gear mechanism and transmitted to the driven shaft 5. The rotation of the driven shaft 5 is further decelerated by a gear reduction mechanism having a mechanical brake device and transmitted to the load sheave 33.

Next, when the electromagnetic coil 9 is energized, as shown in FIG. 25, bearing 2
6. Since the control member 7 is moved forward via the support ring 28 and the tightening spring 31, the control member 7
The annular friction plate 22 of the annular disk body 16 separates from the friction surface 21 of the transmission frame 8, and the frictional engagement between the control member 7 and the transmission frame 8 is released,
and a frusto-conical cylindrical friction ring 18 of the annular disk body 16
is pressed against the frusto-conical friction surface 14 of the annular support member 4, and the annular support member 4 and the control member 7 are frictionally coupled.

When the electric motor 10 with an electromagnetic brake is operated in this state, the annular support member 4, planetary gear 3, control member 7, and internal gear 6 are rotated together by the drive shaft 1, so the driven shaft 5 is rotated at high speed. That is, the rotation of the driven shaft 5 is rotated at the same speed as the drive shaft 1, and the rotation of the driven shaft 5 is reduced by the gear reduction mechanism and transmitted to the load sheave 33.
3 is rotated at relatively high speed.

4 and 5 show a second embodiment of the present invention, in which an annular holding member 23 having an electromagnetic coil 9 fitted and fixed thereon is in contact with the front surface of a rear frame 36 of a transmission frame 8. bolt 2
Electric motor 10 fixed by 4 and equipped with an electromagnetic brake
The drive shaft 1 connected to the rotor shaft 11 is supported by a rear frame 36 via a bearing 37 and is inserted through an annular holding member 23, with a control member made of a magnetic material disposed at the front of the annular holding member 23. 7 is fitted onto the drive shaft 1 via a bearing 38, and an internal gear 6 is provided on the inside of the front end of the control member 7, and an internal gear 6 is provided on the outside of the front end of the control member 7. A frusto-conical cylindrical friction ring 18 is fixed, and an annular friction plate 22 is fixed to the rear surface of the control member 7 and is detachably engaged with the front friction surface of the annular holding member 23. The annular friction plate 22 constitutes a detachable control coupling part.

An annular support member 4 arranged in front of the control member 7
is fitted onto the front end of the drive shaft 1 via a bearing 39, and is fitted onto the rear end of the annular support member 4 into which the truncated conical cylindrical friction ring 18 is removably fitted. A surface 14 is provided, the frusto-conical friction surface 14 and the frusto-conical cylindrical friction ring 18 forming a removable coupling connection.

A planetary gear 3 that meshes with the sun gear 2 and the internal gear 6 provided at the front of the drive shaft 1 is rotatably attached to the rear part of the annular support member 4, and is attached to the drive shaft 1 within the annular holding member 23. The rear part of the fitted thrust bearing 40 is engaged with the stepped portion of the drive shaft 1, and the thrust bearing 40 is fitted onto the drive shaft 1.
A tightening spring 31 is interposed in a compressed state between the spring bearing ring 41 and the control member 7, which are engaged with the front part of the spring bearing ring 41, and is further unrotatably fitted to the rear end of the driven shaft 5. The coupled coupling ring 42 is supported by the frame of the electric chain block via a bearing 43, and the coupled coupling ring 42 and the annular support member 4 are non-rotatably connected via a coupling ring 44.

Note that the transmission mechanism between the driven shaft 5 and the load sheave 33 is the same as that in the first embodiment.

In the device of the second embodiment, when the electromagnetic coil 9 is excited, the control member 7 is attracted and moved rearward against the force of the tightening spring 31, as shown in FIGS. 4 and 5. The frusto-conical cylindrical friction ring 18 of the member 7 is separated from the frusto-conical friction surface 14 of the annular support member 4, and the friction plate 22 at the rear end of the control member 7 is pressed against the front surface of the annular retaining member 23. , the control member 7 and the annular holding member 23 are frictionally coupled.

When the electric motor 10 with an electromagnetic brake is operated in this state, the rotation of the drive shaft 1 is decelerated by the planetary gear mechanism and transmitted to the driven shaft 5 as described above.

Next, when the electromagnetic coil 9 is demagnetized, the tightening spring 3
The control member 7 is moved forward by the force of 1, the annular friction plate 22 of the control member 7 is separated from the annular holding member 23, and the truncated conical cylindrical friction ring 18 of the control member 7 is moved forward by the annular support member 4. Pressed against the conical friction surface 14, the annular support member 4 and the control member 7 are frictionally connected. When the electric motor 10 with an electromagnetic brake is operated in this state, the annular support member 4, the planetary gear 3, and the control member 7 are rotated together by the drive shaft 1, so that the driven shaft 5 rotates at a high speed, that is, the drive shaft 1 rotates at the same speed as

〔Effect of the invention〕

Since this invention is configured as described above,
This produces the effects described below.

Since the sun gear 2 is formed around the drive shaft 1 in the two-stage planetary gear transmission, it is possible to reduce the diameter of the sun gear 2 and increase the reduction ratio of the two-stage planetary gear transmission. The rotation of the driven shaft 5, which has been decelerated by the planetary gear type two-stage transmission, is further decelerated by the gear reduction mechanism and transmitted to the load sheave 33. Therefore, the rotation of the driven shaft 5, which is decelerated by the planetary gear type two-stage transmission, is further decelerated by the gear reduction mechanism and transmitted to the load sheave 33. A hollow shaft 34 having a load sheave 33 can be rotated to transport objects up or down at extremely low speeds using an electric chain block.
A planetary gear type two-stage transmission is disposed on one end side, and a gear reduction mechanism is disposed on the other end side of the hollow shaft 34, so that the gear reduction mechanism is disposed above the load sheave 33 in the casing of the electric chain block. It is possible to improve the weight balance when suspending and supporting the vicinity.

Furthermore, the control mechanism for forward rotational speed switching and reverse rotational speed switching of the planetary gear type transmission is relatively simple and can be controlled accurately, and it is possible to control the switching between high-speed forward rotational speed and high-speed reverse rotational speed. In this case, the large mass portion consisting of the annular support member 4, planetary gear 3, control member 7, internal gear 6, etc. is connected to the drive shaft 1.
Since the rotation is started by , it is possible to start the engine slowly, and therefore the shock when starting at high speed can be reduced.

[Brief explanation of the drawing]

1 to 3 show a first embodiment of the present invention, in which FIG. 1 is a partially cutaway vertical side view of an electric chain block having a two-stage planetary gear transmission, and FIG. FIG. 3 is a longitudinal side view showing a state in which the planetary gear type two-stage transmission is switched to low-speed rotation, and FIG. 3 is a longitudinal side view showing the state in which the planetary gear-type two-stage transmission is switched to high-speed rotation. 4 and 5 show a second embodiment of the present invention, in which FIG. 4 is a partially cutaway vertical side view of an electric chain block having a two-stage planetary gear transmission, and FIG. The figure is a longitudinal side view showing a state in which the planetary gear type two-stage transmission is switched to low speed rotation. In the figure, 1 is a drive shaft, 2 is a sun gear, 3 is a planetary gear, 4 is an annular support member, 5 is a driven shaft, 6 is an internal gear, 7 is a control member, 8 is a transmission frame, 9 is an electromagnetic coil , 10 is an electric motor with an electromagnetic brake, 14 is a frusto-conical friction surface, 18 is a frusto-conical cylindrical friction ring, 21 is a friction surface, 22 is an annular friction plate, 23 is an annular holding member, 25 is an annular member made of magnetic material The body to be attracted, 31 is a tightening spring, 32 is a return spring, 33 is a load sheave, 34 is a hollow shaft, 45 is a frame, and 49 is a chain block support fitting.

Claims (1)

[Claims] 1. A sun gear 2 is formed around the drive shaft 1, and a driven shaft 5 is rotatably inserted into a hollow shaft 34 equipped with a load sheave 32 around which a load chain is wound. An annular support member 4 rotatably supported is non-rotatably connected to one end of a driven shaft 5 protruding from one end of the hollow shaft 34, and includes an internal gear 6 meshing with the planetary gear 3. A control member 7 is rotatably and slidably fitted to the drive shaft 1, and the control member 7 includes a removable connection coupling portion to the annular support member 4 and a transmission frame 8.
A removable braking coupling part is provided for a fixed part, such as, by excitation and demagnetization of one electromagnetic coil 9, the coupling of the control member 7 to the annular support member 4 and the release of the control member 7 from the fixed part. defection and
The other end of the driven shaft 5 protrudes from the other end of the hollow shaft 34 and is configured such that the control member 7 is coupled to the fixed portion and the control member 7 is separated from the annular support member 4. An electric chain block having a two-stage planetary gear transmission, characterized in that a gear reduction mechanism is provided between the other end of the hollow shaft 34.